JP2001199254A - Lateral driving force distributor for vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent generation of cavitations, noises and the like by keeping the inside of a hydraulic motor in a positive pressure condition by supplying oil in an inertia rotation time of the hydraulic motor. SOLUTION: On the central side of the hydraulic motor 18, an oil sump chamber 33 is formed between a motor case 19 and a cylinder block 25. In the cylinder block 25, a plurality of oil passages 34 communicating the oil sump chamber 33 with respective hydraulic chambers 28 individually are arranged, and in the middle of each oil passage 34, a check valve 35 is arranged. When inertia rotation of the hydraulic motor 18 is carried out by means of external force and one of the plurality of hydraulic chambers 28 tends to be a negative pressure, the check valve 35 is automatically opened in the middle of the oil passage 34 communicated to this hydraulic chamber 28. In this way, the oil inside the oil sump 33 can be fed into the hydraulic chamber 28, so that the inside of the hydraulic motor 18 can be kept in a positive pressure condition.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a left and right driving force distribution device for a vehicle, which is preferably used for distributing a driving force from an engine to left and right wheel shafts serving as driving wheels of the vehicle. The present invention relates to a vehicle left / right driving force distribution device configured to positively distribute driving force using a hydraulic motor.

[0002]

2. Description of the Related Art Generally, a vehicle such as a four-wheeled vehicle has left and right driving wheels to improve cornering performance.
A differential gear device including a differential mechanism such as a differential gear is provided between the right wheel shafts, and the driving force from the engine is distributed to the left and right wheel shafts by the differential gear device.

[0003] However, in such a distribution control of the driving force by the differential gear device, the driving force from the engine is distributed to the left and the right using the reaction force or the like that the left and right wheels receive from the road surface. For example, when the wheels slip on a low μ road surface having a reduced friction coefficient due to freezing or the like, stable control of driving force distribution may be difficult.

In order to stably distribute the driving force of the vehicle to the left and right wheel shafts, an auxiliary motor such as a hydraulic motor is incorporated in the differential gear device, and the driving force suitable for the driver's steering operation or the like is provided. Is actively distributed to the left and right wheel shafts (for example, Japanese Patent Laid-Open No. 3-50028).
JP-A-10-329572, etc.).

[0005] A vehicle driving force distribution device according to this type of prior art is provided with a housing, an input shaft provided on an input side of the housing and rotationally driven by an engine of the vehicle, and an input shaft provided on an output side of the housing. A differential mechanism including a differential gear for distributing and transmitting the driving force from the input shaft to the left and right wheel shafts, and pressure oil is supplied and discharged from the outside provided with the differential mechanism on the output side of the housing. Thus, a reversible hydraulic motor or the like that applies a relative rotational force between the left and right wheel shafts.

[0006] When hydraulic oil is supplied and discharged from an external hydraulic source according to the operating state of the vehicle, the relative rotational force between the left and right wheel shafts is generated by this hydraulic motor. The driving stability of the vehicle is ensured by controlling the distribution of the driving force to give the vehicle, for example, by positively generating a yaw moment in the vehicle.

[0007]

By the way, according to the above-mentioned prior art, for example, when one of the wheels spins (slip) while traveling on a low μ road or the like where the road surface is frozen, or when the vehicle turns sharply, When a wheel on the inner side of the turn lifts off the road surface and idles, for example, the hydraulic motor is inertially rotated by the wheel shaft on the idle side, which may cause a pump action.

In such a case, for example, the supply amount of the pressure oil is insufficient in a cylinder serving as a hydraulic chamber of the hydraulic motor, and a negative pressure is easily generated in the supply / discharge passage of the pressure oil of the hydraulic motor. Therefore, not only does it cause cavitation, but it also causes abnormal noise due to air mixing.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problems of the prior art, and it is an object of the present invention to efficiently replenish oil fluid during the inertial rotation of a hydraulic motor and to maintain a positive pressure inside the hydraulic motor. Accordingly, it is an object of the present invention to provide a vehicle left / right driving force distribution device capable of preventing generation of cavitation, abnormal noise, and the like, and improving the life of the hydraulic motor and the reliability of the device.

[0010]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention provides a housing, an input shaft provided on an input side of the housing and rotationally driven by a vehicle engine, and an output side of the housing. And a differential mechanism for distributing and transmitting the driving force from the input shaft to the left and right wheel shafts, and the differential mechanism is provided on the output side of the housing together with the differential mechanism to supply and discharge pressure oil from outside. Thus, the present invention is applied to a left-right driving force distribution device for a vehicle including a reversible hydraulic motor that applies a relative rotational force between the left and right wheel shafts.

The first aspect of the present invention is characterized in that an oil reservoir for storing an oil liquid to be supplied to the hydraulic motor and a hydraulic chamber of the hydraulic motor for supplying and discharging the pressure oil. And a check valve provided in the communication passage to allow the flow of the oil liquid from the oil storage chamber toward the hydraulic chamber and to prevent a reverse flow. I did it.

With this configuration, when the hydraulic motor is inertially rotated by the external force and the hydraulic chamber side becomes negative pressure,
The check valve is opened, the oil liquid in the oil sump chamber can be supplied to the hydraulic chamber, and the inside of the hydraulic motor can always be maintained at a positive pressure. In addition, during normal rotation of the hydraulic motor, the hydraulic motor can be driven to rotate by pressure oil supplied and discharged from an external oil pressure source, and the check valve can be kept closed by the pressure of the pressure oil. It can prevent backflow to the side.

According to the second aspect of the present invention, the hydraulic motor includes an outer rotating body rotatably provided on the output side of the housing, and a pressure oil supplied to the hydraulic chamber rotatably provided in the outer rotating body. An inner rotating body that rotates relative to the outer rotating body by being discharged is configured such that the outer rotating body also serves as a part of one of the left and right wheel shafts.

This eliminates the need to penetrate the wheel shaft on the center side of the hydraulic motor and eliminates the need to provide a space for forming an oil reservoir in the outer rotating body of the hydraulic motor that also serves as one wheel shaft. At the same time, the entire hydraulic motor including the oil reservoir can be housed compactly in the housing.

Further, the invention of claim 3 is configured such that the other one of the left and right wheel shafts is connected to the inner rotating body of the hydraulic motor so as to be integrally rotatable. Thereby, between the one wheel axle composed of the outer rotating body of the hydraulic motor and the other wheel axle connected to the inner rotating body, it is possible to apply mutually opposite rotational forces when the hydraulic motor is rotationally driven, Appropriate driving force can be distributed to the left and right wheel shafts.

According to the fourth aspect of the present invention, the oil reservoir is formed between the outer rotating body and the inner rotating body at the rotation center side of the hydraulic motor. Thus, the oil reservoir can be formed compactly between the outer rotary member and the inner rotary member at the rotation center side of the hydraulic motor, and the housing of the device can be prevented from becoming larger than the oil reservoir.

According to the fifth aspect of the present invention, the outer rotating body of the hydraulic motor is a motor case formed as a stepped cylindrical body with a lid closed at the joint side connected to one wheel as a lid. The inner rotating body has a plurality of cylinders serving as hydraulic chambers, and is constituted by a cylinder block that is rotationally driven in the motor case by a piston provided in each of the cylinders.

Thus, when pressure oil is supplied to and discharged from the cylinders of the cylinder block, the respective pistons are reciprocated in these cylinders, and the reciprocation of each piston causes a relative movement between the motor case and the cylinder block. It is possible to generate an effective rotational force.

According to a sixth aspect of the present invention, an oil reservoir is formed between the lid of the motor case and the cylinder block, and the communication passages are respectively formed in the cylinder block and one end thereof communicates with the oil reservoir. The other end is constituted by a plurality of oil passages individually communicating with each cylinder.

Thus, the oil reservoir can be formed compactly between the cover of the motor case and the cylinder block.
The oil reservoir and the plurality of cylinders can be independently communicated with each other by respective oil passages.

According to a seventh aspect of the present invention, a check valve is provided.
A stepped cylindrical valve cylinder provided in the middle of the communication passage and having a valve seat therein, and a valve lid formed with an oil hole for forming a valve chamber between the valve cylinders and flowing an oil liquid, A valve body that is movably provided in the valve chamber between the valve lid and the valve cylinder, and that is detachably seated on the valve seat.

In this case, if the pressure in the hydraulic chamber becomes negative due to the inertial rotation of the hydraulic motor, the valve element is separated from the valve seat of the valve cylinder, so that the oil liquid in the oil reservoir chamber flows to the hydraulic chamber. Therefore, the inside of the hydraulic motor can be maintained in a positive pressure state.
Also, during normal rotation of the hydraulic motor, the valve element is pushed by pressure oil supplied and discharged from an external hydraulic source, and the valve element is seated on the valve seat, so that the flow of the oil liquid can be prevented, and The hydraulic chamber can be kept at a high pressure.

Further, according to the invention of claim 8, the valve element is formed of a spherical ball valve element, and the valve cover guides the ball valve element to the valve seat so as to be detachable from the valve seat. It has a configuration having a guide projection protruding toward the same. Thus, the ball valve body can be guided in the valve chamber using the guide projection of the valve lid, and the ball valve body can be smoothly separated from and seated on the valve seat.

[0024]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of a vehicle driving force distribution device according to an embodiment of the present invention; FIG.
Will be described in detail.

In the drawing, reference numeral 1 denotes a housing of the driving force distribution device. The housing 1 has a stepped cylindrical input housing portion 2 located on the input side and an input housing portion 2 located on the output side. And a stepped cylindrical output housing portion 3 extending in the left and right directions. The output housing portion 3 has a cylindrical body portion 3A located at the center as shown in FIG. It is generally constituted by stepped cylindrical covers 3B and 3C provided on both the left and right sides of the body 3A.

The output housing portion 3 is provided with a stepped cylindrical portion 3D located inside the body portion 3A and between the cover portion 3C and the cover portion 3C. A hydraulic motor 18 described later is rotatably provided. And
The stepped tubular portion 3D extends in the axial direction from the cover portion 3C side toward the cover portion 3B side, and the distal end side of the stepped tubular portion 3D is formed with a reduced diameter so as to avoid interference with an input gear 4A described later. ing.

Reference numeral 4 denotes a propulsion shaft as an input shaft rotatably provided in the input housing portion 2 of the housing 1,
The propulsion shaft 4 is connected to a crankshaft (not shown) of an engine mounted on the vehicle, and is driven to rotate by the engine. The propulsion shaft 4 is provided with an input gear 4A on the distal end side of the output housing 3 extending into the body 3A, and the input gear 4A meshes with a ring gear 7 described later.

Numeral 5 is a differential mechanism which is rotatably provided in the output housing part 3 located on the cover 3B side. The differential mechanism 5 is constituted by, for example, a planetary gear device or the like, and forms an outer shell thereof. A ring gear 7 meshing with the input gear 4A is fixedly provided with bolts or the like on the outer peripheral side of the differential case 6 (hereinafter, referred to as a differential case 6). The differential case 6 is rotationally driven by the propulsion shaft 4 via the input gear 4A and the ring gear 7, and the driving force at this time is distributed to the left and right wheel shafts 16 and 17 by the sun gear 13 and the carrier 8 described later. Is transmitted.

Here, the differential mechanism 5 is provided so as to be relatively rotatable inside the differential case 6 with an internal gear 6A formed over the entire circumference on the inner peripheral side of the differential case 6 as shown in FIGS. , A plurality of planetary gears 10, 10,... Rotatably supported by the carrier 8 via a support shaft 9 and meshing with the internal gear 6 </ b> A, and the carrier 8 is meshed with the respective planetary gears 10. The other planetary gears 12, 12,... Rotatably supported via the support shaft 11, and the sun gear 1 meshed with each of the planetary gears 12 and relatively rotatable with respect to the carrier 8.
And 3.

The sun gear 13 is connected to a wheel shaft 16 described later.
The rotation of the differential case 6 (for example, the rotation in the direction indicated by the arrow A in FIG. 4) is transmitted to the sun gear 13 via the two planetary gears 10 and 12 as the same rotation. . In addition, the revolution of each of the planetary gears 10 and 12 is transmitted to the carrier 8 via the support shafts 9 and 11, whereby the carrier 8 also rotates in the same direction as the differential case 6.

When the vehicle travels straight, the rotational force of the differential case 6 is evenly distributed to the sun gear 13 and the carrier 8 via the planetary gears 10 and 12, so that the sun gear 13 and the carrier 8 have the same rotation. Left and right wheel axles 1
6 and 17 are driven to rotate.

During steering operation (turning) of the vehicle, the left and right wheels (not shown) rotate so that one of the wheel shafts 16 and 17 rotates faster than the other due to a reaction force or the like received from the road surface. The rotational force of the differential case 6 is transmitted to the gear 13 and the carrier 8 with different rotational ratios. As a result, the wheels on the inside of the turn have a relatively low rotation speed, and the wheels on the outside of the turn have a higher rotation speed, thereby exhibiting a differential function of improving the cornering performance and the like of the vehicle.

Reference numeral 14 denotes a stepped sleeve which constitutes a part of the differential mechanism 5, and the stepped sleeve 14 uses bolts 15 (see FIG. 4) on the end face side of the carrier 8 as shown in FIG. The carrier 8 is fixed and rotates the motor case 19 described later.
(Wheel shaft 17) side.

A spline 14A is formed on the outer periphery of the stepped sleeve 14 on the distal end side, and the spline 14A transmits rotation by being connected to a tubular connecting portion 22B of the other case 22 described later. . A small-diameter oil path 14B extending in the axial direction is formed in the stepped sleeve 14, and the oil path 14B is formed by a drain oil of a hydraulic motor 18 or the like with a stepped shaft portion 16D of a wheel shaft 16 described later and a stepped sleeve 14B. For lubricating between the inner peripheral surface and the inner peripheral surface.

Reference numerals 16 and 17 denote left and right drive wheels (not shown).
The left and right wheel shafts 16 are formed by using a single shaft member, and the right wheel shaft 17 is constituted by a motor case 19 and a joint flange 24 described later. I have. The wheel shaft 16 has a small-diameter spline shaft portion 16A at one end inserted into the output housing portion 3, and the spline shaft portion 16A is prevented from rotating into a stepped hole 25A of a cylinder block 25 described later. Are linked.

The other end of the wheel shaft 16 protruding out of the output housing portion 3 becomes a large-diameter joint flange portion 16B, and another spline shaft is provided at an intermediate portion between the joint flange portion 16B and the spline shaft portion 16A. A portion 16C and a circular stepped shaft portion 16D are formed. The spline shaft portion 16C is inserted and fitted on the inner peripheral side of the sun gear 13 so as to rotate integrally with the sun gear 13, and transmits the rotation of the sun gear 13 to the joint flange portion 16B side of the wheel shaft 16. The joint flange 16B is connected to the left wheel (not shown).

For this reason, the wheel shaft 16 is connected to the joint flange 1.
A portion extending from 6B to the spline shaft portion 16C has a relatively large diameter, and has sufficient rigidity to transmit a large driving force to an external wheel (drive wheel). On the other hand, the stepped shaft portion 16
The portion extending from the position D to the front end side spline shaft portion 16A is formed to have a relatively small diameter because only a relatively small driving force generated in the cylinder block 25 of the hydraulic motor 18 described later needs to be transmitted. . Also, the stepped shaft portion 16
A seal member 48 described later is in sliding contact with the outer peripheral side of D.

Numeral 18 denotes a reversible hydraulic motor located on the cover 3C side and rotatably provided in the output housing 3. The hydraulic motor 18 is, for example, a radial piston type hydraulic motor. Motor case 19,
It comprises a cylinder block 25, a piston 27, a passage block 40 and the like.

Further, the hydraulic motor 18 is disposed in the output housing portion 3 side by side in the left and right directions with respect to the differential mechanism 5, and the passage block 40 is housed between the cylinder block 25 and the differential mechanism 5. It has a configuration. The hydraulic motor 18 rotates the motor case 19 and the cylinder block 25 relative to each other by supplying and discharging pressure oil, and applies a relative rotational force between the left and right wheel shafts 16 and 17. .

Reference numeral 19 denotes a motor case which is rotatably provided in the output housing portion 3 and constitutes an outer rotating body of the hydraulic motor 18. The motor case 19 has a closed cylindrical shape as shown in FIGS. One-sided case 20 formed as a body and integrally formed with an output shaft portion 20B on the center side of the lid portion 20A.
And a cam ring 21 and the other side case 22,
The cam ring 21 is sandwiched and integrated between one side case 20 and the other side case 22 by using a plurality of bolts 23, 23,... (See FIG. 5).

Then, one side case 20, cam ring 21
And the entire motor case 19 composed of the other side case 22 is moved from the position of a cylindrical connecting portion 22B to be described later to the output shaft portion 20.
It is formed as a stepped cylindrical body with a lid extending in the axial direction over the position B, and constitutes the right wheel shaft 17 together with the outer joint flange 24. In this case, the output shaft portion 20B of the one side case 20 protrudes outward from the cover portion 3C of the output housing portion 3, and a joint flange 24 is spline-connected to the protruding end side. The joint flange 24 serves as a joint and is connected to the right wheel (not shown).

Here, the cam ring 2 of the motor case 19
1, a cam surface 21A is formed on the inner peripheral side as shown in FIG. 5, and the cam surface 21A receives a driving force from a piston 27 via each roller 30 described later, thereby forming a connection with the motor case 19. A relative rotational force is generated between the cylinder block 25 and the arrow A direction or the arrow B direction in FIG.

As shown in FIG. 3, the other side case 22 is formed as a stepped cylindrical body whose diameter is reduced in approximately two steps, and is sandwiched between the one side case 20 and the cylinder block 25 toward the differential mechanism 5 side. And a cylindrical connecting portion 22B extending from the distal end of the cylindrical extending portion 22A toward the outer peripheral side of the stepped sleeve 14. . The inner peripheral side of the cylindrical connecting portion 22B is engaged with the spline 14A of the stepped sleeve 14, and the motor case 19 (wheel shaft 17) is integrally rotated with the stepped sleeve 14 of the differential mechanism 5. .

Reference numeral 25 denotes a cylinder block constituting an inner rotating body of the hydraulic motor 18. The cylinder block 25 is formed as a rotor composed of a flat stepped cylindrical body, and is rotated in the motor case 19 via a plurality of bearings. It is provided as possible. A stepped hole 25A is provided in the center of the cylinder block 25 so as to penetrate in the axial direction.
The spline shaft portion 16A of the wheel shaft 16 is connected to the small diameter portion side of A.

Here, FIG.
A plurality of radially extending cylinders 26, 2
Are formed, and each cylinder 26 has a piston 2
7, 27,... Are slidably inserted respectively. In each cylinder 26, a hydraulic chamber 2 is provided by a piston 27.
8 are defined, and in each hydraulic chamber 28, an oil passage 29 described later is provided.
The pressure oil is supplied and discharged via the. Each piston 27 reciprocates in the cylinder 26 by the pressure oil supplied and discharged into the hydraulic chamber 28, and generates the torque of the hydraulic motor 18.

Are a plurality of oil passages formed independently of each other in the cylinder block 25. Each of the oil passages 29 is connected to each of the hydraulic chambers 28 (cylinder 26) so as to be individually communicated with each other. Are provided at regular intervals in the inside, and supply / discharge passages 42A, 4
By sequentially communicating with 2B, pressure oil from the outside is supplied to and discharged from each hydraulic chamber 28.

Are rollers rotatably provided at the protruding end of each piston 27 via a support shaft 31;
Are springs that urge the rollers 30 toward the cam surface 21A of the cam ring 21. The springs 32 are disposed between the cylinder 26 and the piston 27, and project the piston 27 from the cylinder 26. It is always biased in the direction to be. And the roller 30 is the cam ring 21
Slides along the cam surface 21A of the cylinder block 25.
And the cam ring 21 (motor case 19).

Reference numeral 33 denotes an oil sump chamber located between the motor case 19 and the cylinder block 25 at the center side of the hydraulic motor 18, and the oil sump chamber 33 is provided with a motor as shown in FIGS. Lid 20 of case 19 (one side case 20)
A is formed between A and the stepped hole 25A of the cylinder block 25, and contains therein a working oil for the hydraulic motor 18 in a substantially full state.

In this case, part of the pressure oil supplied to each hydraulic chamber 28 of the cylinder block 25 is
Drain oil usually leaks slightly from between the piston and the piston 27, and the drain oil lubricates the sliding surface of the hydraulic motor 18 and the like. Then, the inside of the oil reservoir chamber 33 is kept full of the oil liquid by the drain oil or the like. The hydraulic motor 18 is provided with a drain pipe (not shown) connected to a reservoir 49 described later, and by flowing the drain oil to the reservoir 49 side, the pressure of the oil reservoir chamber 33 (drain oil) is increased. Is maintained at a pressure substantially equal to that in the reservoir 49.

Numerals 34, 34,... Are oil passages as communication passages for individually communicating the hydraulic chambers 28 of the hydraulic motor 18 with the oil reservoir chamber 33.
Are formed as stepped holes extending in the axial direction, and are arranged in the circumferential direction of the cylinder block 25 at intervals corresponding to the respective cylinders 26.

As shown in FIG. 7, one end of the oil passage 34 serves as a valve mounting hole 34A, which opens to the end surface of the cylinder block 25, and communicates with the oil reservoir chamber 33. The other end of the oil passage 34 communicates with the oil passage 29 in the vicinity of the hydraulic chamber 28 to replenish the oil in the oil reservoir 33 into the hydraulic chamber 28 when a check valve 35 described later is opened. is there.

Are valve mounting holes 3 in each oil passage 34.
4A, each check valve 35 is provided.
As shown in FIG. 7 to FIG. 9, the valve is constituted by a valve cylinder 36 formed in a stepped cylindrical shape, a valve lid 37 and a ball valve body 39 described later, and the like. On the inner peripheral side of the valve cylinder 36, a hexagonal square hole 36A located on one side in the axial direction, and a small-diameter oil hole 3A located between a valve chamber 38 and the square hole 36A described later.
6B is formed, and the end of the oil hole 36B is connected to the ball valve body 39.
36C.

The valve cylinder 36 has a threaded portion 36D on the outer peripheral side.
And the external thread portion 36D is connected to the valve mounting hole 34A of the oil passage 34.
Is screwed into the cylinder block 2 so that
5 is attached as shown in FIG. In this case, a tool (not shown) such as a wrench is engaged with the square hole 36A of the valve cylinder 36, and the valve cylinder 36 is removably mounted in the valve mounting hole 34A using this tool.

Numeral 37 denotes a valve cover which is mounted in the valve mounting hole 34A together with the valve cylinder 36. The valve cover 37 is made of a soft metal material such as copper or the like and has a disk having an outer diameter substantially corresponding to the valve cylinder 36. It is formed as. The valve lid 37 is clamped between the rear end portion of the valve mounting hole 34A and the valve cylinder 36 with a tightening margin, and has a function of sealing between the two in a liquid-tight manner. Further, the valve cover 37 forms a valve chamber 38 between itself and the valve cylinder 36 by closing the other end surface of the valve cylinder 36.

Here, a guide projection 37A is integrally provided on the center side of the valve lid 37, and the guide projection 37A is
8, and guides the ball valve body 39 so that it can be detached from and seated on the valve seat 36C. Further, a pair of oil holes 37B, 37B are formed in the valve cover 37 at a position radially outward of the guide projection 37A, and each of the oil holes 37B is a ball valve body 39 similar to the oil hole 36B of the valve cylinder 36. It is formed with a smaller diameter than that. The oil hole 37B communicates the interior of the valve chamber 38 with the oil passage 34 on the hydraulic chamber 28 side to compensate for the opening and closing operations of the ball valve body 39 as described later.

Reference numeral 39 denotes a ball valve as a valve member which is located between the valve cylinder 36 and the valve cover 37 and is movably provided in the valve chamber 38. The ball valve member 39 is made of a steel ball or the like. , Valve cylinder 3
6 is accommodated in the valve chamber 38 so as to be separated from and seated on the valve seat 36C. Then, while the inside of the hydraulic chamber 28 is maintained at a high pressure, the ball valve body 39 is seated on the valve seat 36C by receiving the pressure in the valve chamber 38, and the pressure oil on the hydraulic chamber 28 side is oiled. It prevents backflow to the storage chamber 33 side.

On the other hand, when the pressure in the hydraulic chamber 28 becomes negative due to the inertial rotation of the hydraulic motor 18 as will be described later, the ball valve element 39 separates from the valve seat 36C and the oil hole 36B in the valve cylinder 36.
To allow the oil liquid in the oil reservoir 33 to flow toward the hydraulic chamber 28 via the oil passage 34. This allows
In the hydraulic chamber 28, oil is supplied from the oil passage 34 side in addition to the oil passage 29, so that the inside of the hydraulic chamber 28 can be maintained in a positive pressure state.

Reference numeral 40 denotes each hydraulic chamber 2 of the cylinder block 25.
The passage block 40 is formed as a stepped cylinder as shown in FIGS. 2 and 3 and is located on the outer peripheral side of the wheel shaft 16. The motor case 19 is provided in the tubular extension portion 22A in a detented state using, for example, a knock pin 41 (see FIG. 7). The passage block 40 rotates integrally with the motor case 19, and holds the cylinder block 25 so as to be rotatable relative to the lid 20A of the one-side case 20 or the like.

A plurality of supply / discharge passages 42A, 42B are formed at regular intervals in the circumferential direction in the passage block 40. The supply / discharge passages 42A, 42B are alternately arranged on a virtual circle concentric with the wheel shaft 16. Are alternately arranged. The end faces of the passage block 40 slidably in contact with the end faces of the cylinder blocks 25 are connected to the supply / discharge passages 42A, 4A.
This constitutes a switching valve portion for alternately communicating 2B with each oil passage 29 of the cylinder block 25.

An annular oil groove 43 communicating with each of the supply / discharge passages 42A, 42B is provided on the outer peripheral side of the passage block 40.
A and 43B are formed, and the annular oil grooves 43A and 43B are arranged apart from each other in the axial direction of the passage block 40. The annular oil grooves 43A and 43B are connected to the other case 2
Oil holes 44A, 44B formed in the second cylindrical extension 22A
And a supply / discharge port 45A, 45B formed in the stepped cylindrical portion 3D of the output housing portion 3, and the supply / discharge port 45
The pressure oil from A and 45B is guided to each of the supply and discharge passages 42A and 42B.

Reference numerals 46 and 47 denote sealing members provided between the stepped cylindrical portion 3D of the output housing portion 3 and the motor case 19 of the hydraulic motor 18. The sealing members 46 and 47 are mounted in opposite directions. Fig. 3
As shown in the figure, the sleeve is mounted between the tubular connecting portion 22B of the other side case 22 and the stepped tubular portion 3D with a tight allowance. The seal members 46 and 47 separate, for example, lubricating oil on the differential mechanism 5 side and pressure oil (operating oil) on the hydraulic motor 18 side between the output housing portion 3 and the motor case 19.
It prevents leakage and mixing of these oil liquids.

Reference numeral 48 denotes a seal member provided between the stepped shaft portion 16D of the wheel shaft 16 and the stepped sleeve 14. The seal member 48 is constituted by a double lip seal or the like. Side and stepped shaft portion 16D of wheel shaft 16
It is installed with a tight allowance. The seal member 48 separates, for example, the lubricating oil on the differential mechanism 5 side and the hydraulic oil on the hydraulic motor 18 side between the wheel axle 16 and the motor case 19 to prevent leakage and mixing of these oil liquids. It is to prevent.

Next, 49 is a reservoir in which hydraulic oil is stored, 50 is a hydraulic pump constituting a hydraulic source together with the reservoir 49, and the hydraulic pump 50 is driven to rotate by the propulsion shaft 4 shown in FIG. The hydraulic oil in the reservoir 49 is supplied and discharged to the pipelines 51A and 51B as high-pressure oil.
The distal ends of the conduits 51A, 51B are connected to supply / discharge ports 45A, 45B formed in the stepped cylindrical portion 3D of the output housing portion 3 as shown in FIGS.

Reference numeral 52 denotes a directional control valve provided in the middle of the pipelines 51A and 51B. The directional control valve 52 comprises, for example, an electromagnetic directional control valve having four ports and three positions. The switching means for switching the direction is constituted. The direction control valve 52 has solenoid parts 52A and 52B on both the left and right sides, and the solenoid parts 52A and 52B.
A control signal is output to B from an external control unit (not shown).

As a result, the direction control valve 52 is switched from the neutral position (a) to the left and right switching positions (b) and (c). At these switching positions (b) and (c), the hydraulic pump 50 The direction of the pressure oil supplied to and discharged from the motor 18 is switched. Further, while the direction control valve 52 is kept at the neutral position (a), the supply and discharge of the pressure oil is stopped, thereby substantially stopping the hydraulic motor 18 and invalidating its rotation output.

Reference numeral 53 denotes a variable pressure relief valve. The relief valve 53 is a discharge pressure of the hydraulic pump 50 (pressure of pressure oil).
Is variably controlled.
The relief valve 53 is provided with a solenoid part 5 for pressure adjustment.
3A, and variably controls a relief set pressure according to a current value or a pulse duty of a control signal output from the control unit to the solenoid 53A.

The vehicle left / right driving force distribution device according to the present embodiment has the above-described configuration. Next, the operation thereof will be described.

First, when the vehicle engine is driven to rotate,
This rotation output is transmitted to the differential case 6 of the differential mechanism 5 via the propulsion shaft 4, and the rotation of the differential case 6 (for example, the rotation in the direction of arrow A in FIG. 4) is performed via the two planetary gears 10 and 12. The rotation is transmitted to the sun gear 13 in the same direction. The carrier 8 of the differential mechanism 5 includes the planetary gears 10 and 12
Is transmitted through the support shafts 9 and 11, whereby the carrier 8 also rotates in the same direction as the differential case 6.

When the vehicle travels straight, the rotational force of the differential case 6 is evenly distributed to the sun gear 13 and the carrier 8 via the planetary gears 10 and 12, and the sun gear 13
The carrier and the carrier 8 rotate the left and right wheel shafts 16 and 17 at the same number of revolutions, so that the vehicle is driven to travel through the left and right wheels.

Also, during steering operation (turning) of the vehicle, one of the wheel shafts 16 and 17 rotates faster than the other due to the reaction force or the like received by the left and right wheels from the road surface.
The rotational force of the differential case 6 is transmitted to the sun gear 13 and the carrier 8 with different rotational ratios, whereby
The wheels on the inside of the turn have a relatively low rotation speed, and the wheels on the outside of the turn have a higher rotation speed, so that the cornering performance and the like of the vehicle can be improved.

The distribution of the driving force to the left and right wheel shafts 16 and 17 by the differential mechanism 5 is as follows.
Since the control depends on the reaction force or the like received by the right wheel from the road surface, for example, when a slip occurs, the function of distributing the driving force is lost, and the running stability of the vehicle may not always be improved.

In such a case, a control signal is output from the control unit to the direction control valve 52 and the relief valve 53 in accordance with detection signals from various sensors (not shown) for detecting the driving state of the vehicle. By switching the direction control valve 52 from the neutral position (A) to the switching position (B), the pressure oil from the hydraulic pump 50 is supplied to the pipelines 51A and 51A.
Hydraulic motor 18 in output housing section 3 via 51B
To supply and discharge pressure oil.

The hydraulic motor 18 in the output housing 3 is connected to the supply / discharge passages 42A, 42B of the passage block 40.
When pressure oil is supplied and discharged into each hydraulic chamber 28 in the cylinder block 25 through each oil passage 29 and the like, each cylinder 2
The piston 27 is reciprocated in 6, whereby the motor case 19 of the hydraulic motor 18 and the cylinder block 25 rotate relative to each other.

As a result, between the left and right wheel shafts 16, 17, rotational forces due to the relative rotation of the motor case 19 and the cylinder block 25 are applied in opposite directions. Is positively distributed to the left and right wheel shafts 16 and 17 in accordance with the rotational force of the hydraulic motor 18. By distributing the driving force at this time, for example, a yaw moment can be positively generated in the vehicle, and the running stability of the vehicle can be ensured.

On the other hand, for example, when one of the wheels spins (slip) while traveling on a low μ road or the like on which the road surface is frozen, or when the vehicle makes a sharp turn, the wheel inside the turn is lifted off the road surface and slips. In such a case, the wheel shaft 1 on the idling side
In some cases, the hydraulic motor 18 is inertially rotated by 6 or 17 to cause a pump action.

In such a case, for example, the supply amount of the pressure oil is insufficient in the hydraulic chamber 28 of the hydraulic motor 18 or the like, and the pressure in the hydraulic chamber 28 and the oil passage 29 of the hydraulic motor 18 tends to be negative. Therefore, not only cavitation is easily generated in the hydraulic motor 18 but also noise may be generated due to mixing of air or the like.

Therefore, in the present embodiment, an oil sump chamber 33 is formed between the motor case 19 and the cylinder block 25 at the center of the hydraulic motor 18, and the oil sump is formed in the cylinder block 25. A plurality of oil passages 34, 34,... For individually communicating the chambers 33 with the respective hydraulic chambers 28 are provided, and a check valve 35,
, Are provided, and the hydraulic chambers 28 are provided by the respective check valves 35.
Is configured to control the supply of the oil liquid to the.

Thus, when the hydraulic motor 18 is inertially rotated by an external force and any one of the plurality of hydraulic chambers 28, 28,... Has a negative pressure tendency, the oil passage 34 communicating with the hydraulic chamber 28 On the way, the check valve 35 is automatically opened, the oil liquid in the oil reservoir chamber 33 can be supplied toward the hydraulic chamber 28, and the inside of the hydraulic motor 18 can always be maintained in a positive pressure state.

When the hydraulic motor 18 is rotating normally, the hydraulic motor 18 can be driven to rotate stably by the hydraulic oil supplied and discharged from the external hydraulic pump 50, and the check valve 35 is operated by the pressure of the hydraulic oil. The valve can be kept closed, and the pressure oil can be prevented from flowing back to the oil reservoir chamber 33 side.

In this case, since the check valve 35 is constituted by the stepped cylindrical valve cylinder 36, the valve cover 37, the valve chamber 38 and the ball valve body 39, the structure of the check valve 35 can be simplified, and the check valve 35 can be reduced in size. The weight can be reduced. And valve cover 3
7 is made of a soft metal material such as copper or the like, so that the valve cover 37 is clamped between the valve mounting hole 34A of the oil passage 34 and the valve cylinder 36 with a tight allowance, so that the valve cover 37 has a sealing function. , And the pressure oil in the hydraulic chamber 28 can be prevented from leaking from between the valve mounting hole 34A and the valve cylinder 36.

The ball valve 39 can be movably accommodated in a valve chamber 38 formed between the valve lid 37 and the valve cylinder 36, and the ball valve 39 is separated from the valve seat 36 C of the valve cylinder 36. After being seated, the check valve 35 can be opened and closed. A guide projection 37A is provided on the center side of the valve cover 37 so as to project in the axial direction into the valve chamber 38.
Accordingly, the ball valve element 39 can be guided so as to smoothly separate from and seat on the valve seat 36C, and the opening and closing operations of the ball valve element 39 can be stabilized.

When the pressure in the hydraulic chamber 28 becomes negative due to the inertial rotation of the hydraulic motor 18, the ball valve body 39 can be automatically separated from the valve seat 36C, and the oil liquid in the oil reservoir chamber 33 can be removed. The hydraulic motor 18 can be circulated to the hydraulic chamber 28 via the oil passage 34, and the inside of the hydraulic motor 18 can be maintained in a positive pressure state.

At the time of normal rotation of the hydraulic motor 18,
The ball valve element 39 in the valve chamber 38 is pushed to the valve seat 36C side by the pressure oil supplied and discharged from the external hydraulic pump 50, and the ball valve element 39 is seated on the valve seat 36C, so that the oil liquid flows. And the inside of the hydraulic chamber 28 of the hydraulic motor 18 can be maintained at a high pressure.

In this embodiment, one of the left and right wheel shafts 16 and 17 is connected to the hydraulic motor 18.
Motor case 19 and a joint flange 24, and the motor case 1
9 is spline-coupled at the position of the cylindrical connecting portion 22B, and the output shaft portion 20B integrally formed with the lid portion 20A of the one-side case 20 is splined to the joint flange 24 at a position outside the output housing portion 3. It is configured to be combined.

As a result, the motor case 19 serving as the outer rotating body of the hydraulic motor 18 can also be used as a part of the wheel shaft 17, and it is not necessary to prepare a long wheel shaft separately from the hydraulic motor as in the prior art. . For this reason, the number of parts of the driving force distribution device can be reduced, and workability during assembly can be improved.

Then, the motor case 1 of the hydraulic motor 18
9 can also serve as the wheel shaft 17, so that the hydraulic motor 1
8 does not require a wheel shaft that passes through the motor case 19 and the cylinder block 25 in the axial direction.
Can be formed as a covered cylindrical body, and it is only necessary to fit, for example, a small-diameter end portion (spline shaft portion 16A) of the wheel shaft 16 into the stepped hole 25A of the cylinder block 25 in a detented state. .

As a result, the cylinder block 25 of the hydraulic motor 18 can be formed with a relatively small outer diameter, and the outer diameter of the motor case 19 can be reduced.
For this reason, the hydraulic motor 18 can be stored compactly in the output housing portion 3, and the size and weight of the entire device can be reduced.

On the other hand, with respect to the wheel shaft 16, by forming a relatively large diameter portion from the joint flange portion 16B to the spline shaft portion 16C, sufficient rigidity for transmitting a large driving force to external wheels is provided. be able to. The portion extending from the position of the spline shaft portion 16C to the spline shaft portion 16A on the distal end side is formed to have a relatively small diameter because only a relatively small driving force generated in the cylinder block 25 of the hydraulic motor 18 needs to be transmitted. This eliminates the need for the wheel axle 16 to be formed as a large, sturdy, long shaft as a whole.

The motor case 19 is formed as a stepped cylindrical body having a lid so as to also serve as a part of the wheel shaft 17, and a cylinder block 25 and a differential mechanism are provided in the other case 22 of the motor case 19. The passage block 40 is located between the passage block 40 and the fifth side. And the hydraulic motor 1
Since there is no need to provide a wheel shaft at the center side of the motor shaft 8, there is no capacity between the lid 20 A of the motor case 19 (one side case 20) and the stepped hole 25 A of the cylinder block 25. A space for forming the large oil reservoir chamber 33 can be secured.

The motor case 1 of the hydraulic motor 18
9 and the cylinder block 25, the oil sump chamber 33 can be formed compactly, and the oil sump chamber 33 and the plurality of hydraulic chambers 2 are formed.
,... Can be independently communicated with each other by respective oil passages 34, 34,..., And the supply of oil to each hydraulic chamber 28 can be smoothly controlled by the check valve 35. .

Further, the motor case 1 of the hydraulic motor 18
9, the motor case 19 is formed as a covered cylindrical body, so that, for example, only three seal members 46, 47, and 48 are used, and the lubricating oil on the differential mechanism 5 side is used. The hydraulic oil on the hydraulic motor 18 side can be easily separated, and leakage and mixing of these oil liquids can be satisfactorily prevented.

As a result, it is not necessary to use a part of the pressure oil (hydraulic oil) supplied / discharged to / from the hydraulic motor 18 as the lubricating oil on the differential mechanism 5 side. It can be supplied as lubricating oil to enhance lubrication performance. Also, the working oil supplied to and discharged from the hydraulic motor 18 can be extended in life by using a dedicated oil liquid, thereby improving maintainability.

Therefore, according to the present embodiment, when the hydraulic motor 18 is rotated by inertia, the oil liquid in the oil reservoir chamber 33 is removed from the hydraulic chamber 2.
8 can be efficiently replenished, and the inside of the hydraulic motor 18 can always be maintained in a positive pressure state. Then, it is possible to prevent cavitation and abnormal noise from being generated in the hydraulic motor 18,
The durability and life of the hydraulic motor 18 can be improved, and the reliability as a driving force distribution device can be improved.

Further, since the wheel shaft 17 is also used as the motor case 19 of the hydraulic motor 18, it is not necessary to use a long and sturdy large-diameter shaft member, thereby reducing the number of parts and improving the workability during assembly. can do. Further, the lubricating oil used for the differential mechanism 5 and the like can be satisfactorily separated from the hydraulic oil on the hydraulic motor 18 side, and the lubricating performance can be improved.

In the above embodiment, the check valve 3
Although the case where the ball valve body 39 made of a steel ball or the like is used as the valve body of No. 5 has been described as an example, the present invention is not limited to this. For example, a check valve using a small-diameter poppet valve body is adopted. Alternatively, various types of check valves such as a check valve using a plate-shaped reed valve may be employed.

In the above embodiment, the case where the radial piston type hydraulic motor 18 is used has been described as an example. However, the present invention is not limited to this. For example, a swash plate type hydraulic motor, a trochoid type Various types of hydraulic motors, such as the hydraulic motor described above, may be employed.

Further, in the above-described embodiment, the case where the differential mechanism 5 is constituted by the planetary gears 10, 12 and the like has been described as an example.
The differential mechanism may be configured using a bevel gear or the like in the same manner as in the related art described in Japanese Patent Application Laid-Open No. 50028 and Japanese Patent Application Laid-Open No. 10-329572.

[0098]

As described above in detail, according to the first aspect of the present invention, an oil reservoir for storing an oil liquid to be supplied to the hydraulic motor is provided, and the oil reservoir is provided with the hydraulic chamber of the hydraulic motor. And a check valve is provided in the communication path, so that when the hydraulic chamber side becomes negative pressure due to the inertial rotation of the hydraulic motor, the check valve is opened to open the oil reservoir chamber. The hydraulic fluid can be supplied to the hydraulic chamber side, and the inside of the hydraulic motor can always be kept in a positive pressure state. Therefore,
It is possible to prevent cavitation and abnormal noise from being generated in the hydraulic motor, to improve the durability and life of the hydraulic motor, and to enhance the reliability as a driving force distribution device.

According to the second aspect of the present invention, since one of the left and right wheel shafts is shared by the outer rotating body of the hydraulic motor, the wheel shaft is located at the center of the hydraulic motor. Need not be provided so as to penetrate through, and a space for forming an oil reservoir chamber can be secured in the outer rotating body of the hydraulic motor also serving as a wheel shaft. As a result, the entire hydraulic motor including the oil sump chamber can be housed compactly in the housing, and the size of the device can be reduced.

Further, according to the third aspect of the present invention, the other of the left and right wheel axles is connected to the inner rotating body of the hydraulic motor so as to be integrally rotatable. When the motor is rotationally driven by supplying and discharging pressure oil from the outside to the outside, rotational forces in opposite directions are generated between one wheel shaft composed of the outer rotating body and the other wheel shaft connected to the inner rotating body. , And appropriate driving force distribution can be performed for the left and right wheel shafts.

Further, according to the present invention, the oil reservoir can be formed compactly between the outer rotating body and the inner rotating body located at the center side of the hydraulic motor. It is possible to prevent the housing from being enlarged by the oil sump chamber, and to reduce the size of the entire apparatus.

According to a fifth aspect of the present invention, the outer rotating body of the hydraulic motor is a motor case formed as a stepped cylindrical body with a lid, and the inner rotating body is a hydraulic chamber for supplying and discharging pressure oil. Since it is constituted by a cylinder block which has a plurality of cylinders and is rotatably driven in the motor case by a piston provided in each of the cylinders, when pressure oil is supplied / discharged into a hydraulic chamber formed by each cylinder of the cylinder block The piston can be reciprocated in each cylinder to generate a relative rotational force between the motor case and the cylinder block, and the driving force can be positively distributed to the left and right wheels.

According to a sixth aspect of the present invention, the oil reservoir is formed between the lid of the motor case and the cylinder block, and the communication passages are respectively formed in the cylinder block and one end side is formed in the oil reservoir. Since the other end side of the communication is constituted by a plurality of oil passages which individually communicate with each cylinder, an oil sump chamber can be formed compactly between the lid of the motor case and the cylinder block. Can be communicated with each other independently by respective oil passages, and the occurrence of negative pressure can be prevented independently for each cylinder.

According to the seventh aspect of the present invention, since the check valve is constituted by a stepped cylindrical valve cylinder, a valve cover, and a valve body, the entire check valve has a simple structure and is reduced in size and weight. Therefore, for example, the check valve can be compactly incorporated in the cylinder block.

Further, according to the invention of claim 8,
The valve body is formed of a spherical ball valve body, and the valve cover is provided with a guide projection protruding toward the valve seat side in the valve chamber. The ball valve element can be smoothly guided and seated on and off the valve seat, and the opening and closing operations of the check valve can be stabilized.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing a left-right driving force distribution device for a vehicle according to an embodiment of the present invention.

FIG. 2 is an enlarged longitudinal sectional view showing an output housing portion side in FIG. 1;

FIG. 3 is an enlarged longitudinal sectional view showing a differential mechanism, a hydraulic motor, and the like in FIG. 2;

FIG. 4 is a sectional view showing the differential mechanism in an enlarged manner from arrow IV-IV in FIG. 3;

5 is a cross-sectional view showing the hydraulic motor in an enlarged manner from a direction indicated by arrows VV in FIG. 3;

FIG. 6 is a side view showing the cylinder block together with a plurality of check valves in an enlarged manner from arrow VI-VI in FIG. 3;

FIG. 7 is an enlarged half sectional view showing a main part of the hydraulic motor.

FIG. 8 is an enlarged sectional view showing a state in which a valve cylinder and a valve lid of the check valve are disassembled.

FIG. 9 is a cross-sectional view showing the valve lid from the direction of arrows IX-IX in FIG. 8;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Housing 2 Input housing part 3 Output housing part 4 Propulsion shaft (input shaft) 5 Differential mechanism 6 Differential case 7 Ring gear 16, 17 Wheel shaft 18 Hydraulic motor 19 Motor case (outer rotating body) 20 One side case 20A Lid 21 Cam ring 22 Other side case 22A Cylindrical extension 24 Joint flange (joint) 25 Cylinder block (inner rotating body) 26 Cylinder 27 Piston 28 Hydraulic chamber 33 Oil reservoir chamber 34 Oil passage (communication passage) 35 Check valve 36 Valve cylinder 36C Valve seat 37 Valve lid 37A Guide projection 37B Oil hole 38 Valve chamber 39 Ball valve element (valve element) 40 Passage block 42A, 42B Supply / discharge passage 46, 47, 48 Seal member 49 Reservoir 50 Hydraulic pump (hydraulic power source) 52 Direction Control valve 53 Relief valve

Claims (8)

[Claims] 1. A housing, an input shaft provided on an input side of the housing and rotationally driven by an engine of a vehicle, and a driving force from the input shaft provided on an output side of the housing and applied to left and right wheel shafts. And a differential mechanism that is provided on the output side of the housing together with the differential mechanism to supply and discharge pressure oil from the outside to thereby generate a relative rotational force between the left and right wheel shafts. A left-right driving force distribution device for a vehicle, comprising: a reversible hydraulic motor to be applied; an oil sump chamber containing an oil liquid to be supplied to the hydraulic motor; And a check valve provided in the communication passage for permitting the flow of the oil liquid from the oil reservoir toward the hydraulic chamber and preventing a reverse flow. Vehicle characterized by having Left and right driving force distribution device. 2. The hydraulic motor according to claim 1, wherein an outer rotating body rotatably provided on an output side of the housing, and a pressure oil is supplied to and discharged from the hydraulic chamber rotatably provided in the outer rotating body. 2. The outer rotating body according to claim 1, comprising an inner rotating body that rotates relative to the outer rotating body, wherein the outer rotating body also serves as a part of one of the left and right wheel shafts. 3. Right and left driving force distribution device for vehicles. 3. The left-right driving force distribution device for a vehicle according to claim 2, wherein the other of the left and right wheel shafts is connected to the inner rotating body of the hydraulic motor so as to be integrally rotatable. 4. The left and right driving force distribution of a vehicle according to claim 2, wherein the oil reservoir is formed between the outer rotating body and the inner rotating body and is located at a rotation center side of a hydraulic motor. apparatus. 5. The outer rotating body of the hydraulic motor comprises a motor case formed as a stepped cylindrical body with a lid closed at a joint portion side connected to one wheel and serving as a lid. 5. The vehicle according to claim 2, 3 or 4, comprising a plurality of cylinders serving as the hydraulic chambers, and comprising a cylinder block which is rotationally driven in the motor case by a piston provided in each of the cylinders. Driving force distribution device. 6. The oil reservoir is formed between a lid of the motor case and a cylinder block, and the communication passages are respectively formed in the cylinder block, one end of which communicates with the oil reservoir and the other end of which communicates with the oil reservoir. 6. The vehicle left / right driving force distribution device according to claim 5, wherein the vehicle left / right driving force distribution device includes a plurality of oil passages individually communicating with each cylinder. 7. The check valve according to claim 1, wherein the check valve is provided in the middle of the communication passage and has a valve seat therein, and a valve chamber is formed between the valve cylinder and an oil hole through which the oil liquid flows. 5. A valve cover, comprising: a valve cover provided; and a valve body movably provided in the valve chamber between the valve cover and the valve cylinder and detachably seated on the valve seat. , 5 or 6, the right and left driving force distribution device for a vehicle. 8. The valve body comprises a spherical ball valve body,
8. The vehicle according to claim 7, wherein the valve cover has a guide protrusion protruding toward the valve seat side in the valve chamber to guide the ball valve body so as to be detachable and seatable with respect to the valve seat. Power distribution device.